JP3114438B2 - Rolling bearing - Google Patents
Rolling bearingInfo
- Publication number
- JP3114438B2 JP3114438B2 JP05177568A JP17756893A JP3114438B2 JP 3114438 B2 JP3114438 B2 JP 3114438B2 JP 05177568 A JP05177568 A JP 05177568A JP 17756893 A JP17756893 A JP 17756893A JP 3114438 B2 JP3114438 B2 JP 3114438B2
- Authority
- JP
- Japan
- Prior art keywords
- inner ring
- oil passage
- raceway
- rolling bearing
- present
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
- F16C19/525—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to temperature and heat, e.g. insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Description
【０００１】[0001]
【産業上の利用分野】この発明に係る転がり軸受は、ガ
スタービンやジェットエンジン等の高速回転機械の回転
軸を支承する為に利用する。BACKGROUND OF THE INVENTION rolling bearings according to the present invention is utilized for supporting a rotating shaft of a high speed rotary machine such as a gas turbine or jet engines.
【０００２】[0002]
【従来の技術】回転軸を支承する為に従来から、図８に
示す様な玉軸受、或は図１１に示す様なころ軸受等の転
がり軸受が広く使用されている。先ず、図８に示した玉
軸受は、内周面に外輪軌道１を有する外輪２と、外周面
に内輪軌道３を有する内輪４と、上記外輪軌道１と内輪
軌道３との間に転動自在に設けられた複数の玉５（転動
体）とを備えている。この玉５は、保持器６によって、
円周方向等間隔に保持されている。2. Description of the Related Art Conventionally, ball bearings as shown in FIG. 8 or rolling bearings such as a roller bearing as shown in FIG. 11 have been widely used to support a rotating shaft. First, the ball bearing shown in FIG. 8 has an outer race 2 having an outer raceway 1 on an inner peripheral surface, an inner race 4 having an inner raceway 3 on an outer peripheral surface, and rolling between the outer raceway 1 and the inner raceway 3. And a plurality of balls 5 (rolling elements) provided freely. The ball 5 is held by the cage 6
It is held at equal intervals in the circumferential direction.
【０００３】尚、上記図８に示した玉軸受の場合には、
上記内輪４として二分割式のものを使用している。即
ち、この内輪４は、それぞれが円環状に形成された左右
１対の半片７ａ、７ｂを重ね合わせる事で構成してい
る。上記内輪軌道３はこれら両半片７ａ、７ｂの突き合
わせ部に設けられる。但し、上記各玉５は、鎖線ａで示
す接触角を持ってこの内輪軌道３に当接する為、これら
各玉５の転動面が上記両半片７ａ、７ｂの合わせ面に接
触する事はない。In the case of the ball bearing shown in FIG.
The inner ring 4 is of a two-part type. That is, the inner ring 4 is formed by overlapping a pair of left and right half pieces 7a and 7b each formed in an annular shape. The inner raceway 3 is provided at the butting portion of the two halves 7a and 7b. However, since each of the balls 5 comes into contact with the inner raceway 3 with a contact angle indicated by a chain line a, the rolling surface of each of the balls 5 does not contact the mating surface of the two halves 7a and 7b. .
【０００４】上述の様な半片７ａ、７ｂの内、一方（図
８の左方）の半片７ａには、図９〜１０に示す様な凹溝
８及び通油孔９を形成している。この内の凹溝８は、上
記半片７ａの内端縁に形成されて、他方（図８の右方）
の半片７ｂとの組み合わせ時に、上記内輪軌道３の中央
部に開口する給油通路を構成する。又、上記通油孔９
は、上記一方の半片７ａの軸方向（図８の左右方向）端
部外周面で、上記内輪軌道３から外れた部分に開口して
いる。更に、上記他方の半片７ｂにも通油孔１０を形成
している。この通油孔１０は、上記他方の半片７ｂの軸
方向端部外周面で、上記内輪軌道３から外れた部分に開
口している。[0004] Of the above-mentioned halves 7a and 7b, one (the left side of FIG. 8) half 7a is formed with a concave groove 8 and an oil passage 9 as shown in FIGS. The concave groove 8 is formed on the inner edge of the half piece 7a, and the other groove (right side in FIG. 8).
When combined with the half piece 7b, an oil supply passage opening at the center of the inner raceway 3 is formed. In addition, the oil passage hole 9
Is opened at a portion off the inner raceway 3 on the outer peripheral surface of the end of the one half 7a in the axial direction (left-right direction in FIG. 8). Further, an oil passage hole 10 is also formed in the other half 7b. The oil passage hole 10 is open at a portion off the inner raceway 3 on the outer peripheral surface of the other half piece 7b at the axial end.
【０００５】転がり軸受を組み込んだ高速回転機械の運
転時に、これら凹溝８及び通油孔９、１０には、上記内
輪４の内側に支持した回転軸の側から潤滑油を送り込
む。この結果、前記各玉５と外輪軌道１及び内輪軌道３
との接触部、並びに内輪４外周面と保持器６内周面との
摺接部の潤滑が行なわれる。During operation of a high-speed rotating machine incorporating a rolling bearing, lubricating oil is fed into these concave grooves 8 and oil passage holes 9 and 10 from the side of a rotating shaft supported inside the inner ring 4. As a result, the balls 5 and the outer raceway 1 and the inner raceway 3
And the sliding contact between the outer peripheral surface of the inner ring 4 and the inner peripheral surface of the retainer 6 is lubricated.
【０００６】次に、図１１に示したころ軸受は、内周面
に外輪軌道１ａを有する外輪２ａと、外周面に内輪軌道
３ａを有する内輪４ａと、上記外輪軌道１ａと内輪軌道
３ａとの間に転動自在に設けられた複数のころ１１（転
動体）とを備えている。このころ１１は、保持器６ａに
よって、円周方向等間隔に保持されている。Next, the roller bearing shown in FIG. 11 includes an outer race 2a having an outer raceway 1a on an inner peripheral surface, an inner race 4a having an inner raceway 3a on an outer peripheral surface, and the outer raceway 1a and the inner raceway 3a. A plurality of rollers 11 (rolling elements) are provided between the rollers 11 so as to be freely rotatable. The rollers 11 are held at equal intervals in the circumferential direction by a holder 6a.
【０００７】この様なころ軸受の場合、上記内輪４ａの
軸方向両端部に通油孔９ａ、１０ａを形成し、上記各こ
ろ１１と外輪軌道１ａ及び内輪軌道３ａとの接触部、並
びに内輪４ａ外周面と保持器６ａ内周面との摺接部に潤
滑油を送り込み自在としている。In the case of such a roller bearing, oil passage holes 9a and 10a are formed at both ends in the axial direction of the inner ring 4a, and the contact portions of the rollers 11 with the outer ring raceway 1a and the inner ring raceway 3a and the inner ring 4a. Lubricating oil can be freely fed into a sliding contact portion between the outer peripheral surface and the inner peripheral surface of the retainer 6a.
【０００８】[0008]
【発明が解決しようとする課題】ところが、上述の様に
構成される玉軸受、ころ軸受等の転がり軸受の場合、次
に述べる様な解決すべき点がある。即ち、転がり軸受を
組み込んだ高速回転機械の回転軸と共に内輪４、４ａを
高速回転させた場合、この内輪４、４ａには、遠心力に
基づいて円周方向に亙る引っ張り力が加わる。However, in the case of a rolling bearing such as a ball bearing and a roller bearing configured as described above, there are the following points to be solved. That is, when the inner rings 4, 4a are rotated at high speed together with the rotating shaft of a high-speed rotating machine incorporating rolling bearings, a tensile force is applied to the inner rings 4, 4a in the circumferential direction based on centrifugal force.
【０００９】この引っ張り力に基づき、上記内輪４、４
ａに形成した通油孔９、９ａ、１０、１０ａ部分に応力
集中が生じる。従来の転がり軸受の場合、上記各通油孔
９、９ａ、１０、１０ａの断面形状が何れも円形であっ
た為、上記応力集中が著しく、内輪４、４ａを高速で長
時間回転させた場合には、亀裂等の欠陥を生じる可能性
があった。この為従来は、内輪４、４ａの回転速度を、
上記欠陥を生じない程度に抑えているのが現状である。
図８〜１０の玉軸受に設けた凹溝８の場合には、上述の
様な応力集中が生じにくいが、この凹溝８による給油通
路は、半片７ａ、７ｂ同士の合わせ面にしか設ける事が
できず、通油孔９、９ａ、１０、１０ａの代わりにはな
らない。Based on this pulling force, the inner rings 4, 4
Stress concentration occurs in the oil passage holes 9, 9a, 10, 10a formed in a. In the case of a conventional rolling bearing, since the cross-sectional shape of each of the oil passage holes 9, 9a, 10, 10a is circular, the stress concentration is remarkable, and the inner ring 4, 4a is rotated at high speed for a long time. Had a possibility of causing defects such as cracks. For this reason, conventionally, the rotation speed of the inner rings 4, 4a is
At present, the above defects are suppressed to the extent that they do not occur.
In the case of the grooves 8 provided in the ball bearings of FIGS. 8 to 10, the stress concentration as described above does not easily occur, but the oil supply passage formed by the grooves 8 is provided only on the mating surface between the halves 7a and 7b. And cannot be used in place of the oil holes 9, 9a, 10, 10a.
【００１０】尚、上述の説明は、潤滑油を通す為の通油
孔９、９ａ、１０、１０ａの断面形状に起因して生じる
応力集中に就いて説明したが、この様な応力集中は、通
油孔以外の孔でも生じる。即ち、運転時に内輪４の温度
を測定する為この内輪４に、図１２に示す様な凹孔１
４、１４を形成し、この凹孔１４、１４内に温度センサ
を設置する場合がある。従来の転がり軸受の場合、この
様な凹孔１４、１４の断面形状も通油孔と同様に円形で
あった為、上述の様な応力集中が発生する。本発明の転
がり軸受は、この様な事情に鑑みて発明したものであ
る。In the above description, the stress concentration caused by the cross-sectional shape of the oil passage holes 9, 9a, 10 and 10a for passing the lubricating oil has been described. It also occurs in holes other than oil passage holes. That is, in order to measure the temperature of the inner ring 4 during operation, the inner ring 4 has a concave hole 1 as shown in FIG.
4 and 14 and a temperature sensor may be installed in the concave holes 14 and 14 in some cases. In the case of a conventional rolling bearing, since the cross-sectional shape of the concave holes 14 is circular like the oil passage hole, the above-described stress concentration occurs. The rolling bearing of the present invention has been invented in view of such circumstances.
【００１１】[0011]
【課題を解決するための手段】本発明の転がり軸受は、
前述した従来の転がり軸受と同様に、内周面に外輪軌道
を有する外輪と、外周面に内輪軌道を有する内輪と、上
記外輪軌道と内輪軌道との間に転動自在に設けられた複
数の転動体と、上記内輪の軸方向端部で上記内輪軌道か
ら外れた部分に設けられ、この内輪の内周面と外周面と
を連通させる通油孔とを備え、上記内輪を回転させる状
態で使用する。According to the present invention, there is provided a rolling bearing comprising:
Similarly to the conventional rolling bearing described above, an outer ring having an outer ring raceway on the inner peripheral surface, an inner ring having an inner ring raceway on the outer peripheral surface, and a plurality of rollers provided rotatably between the outer raceway and the inner raceway. A rolling element, and an oil passage hole provided at a portion of the inner ring at an axial end portion deviating from the inner ring raceway and communicating an inner peripheral surface and an outer peripheral surface of the inner ring with each other, in a state where the inner ring is rotated. use.
【００１２】特に、本発明の転がり軸受に於いては、上
記内輪の円周方向に亙る上記通油孔の断面形状を、上記
内輪の円周方向が長く、軸方向が短く、且つ尖った角部
を持たない形状とした事を特徴としている。In particular, in the rolling bearing of the present invention, the cross-sectional shape of the oil passage hole in the circumferential direction of the inner ring is such that the circumferential direction of the inner ring is longer, the axial direction is shorter, and the sharp corner is formed. It is characterized by having no part.
【００１３】[0013]
【作用】上述の様に構成される本発明の転がり軸受の場
合には、内輪が高速回転した場合にも通油孔部分に応力
集中が生じにくい。この結果、各通油孔部分に亀裂等の
欠陥を生じにくくなり、上記内輪をより高速で回転させ
る事が可能となる。In the case of the rolling bearing of the present invention configured as described above, even when the inner ring rotates at high speed, stress concentration hardly occurs in the oil passage hole portion. As a result, defects such as cracks are less likely to occur in each oil passage hole portion, and the inner ring can be rotated at a higher speed.
【００１４】[0014]
【実施例】図１〜２は本発明の第一実施例を示してい
る。尚、本発明の転がり軸受の特徴は、内輪１２に設け
た通油孔１３の断面形状にあり、その他の構成及び作用
は、前述した従来の転がり軸受の場合と同様である。従
って、内輪１２以外の部分に就いては図示並びに説明を
省略し、以下、本発明の特徴部分に就いて説明する。1 and 2 show a first embodiment of the present invention. The feature of the rolling bearing of the present invention, the cross-sectional shape near the oil passing hole 13 provided in the inner ring 12 is, other configurations and functions are the same as those of the conventional rolling bearing described above. Accordingly, illustration and description of parts other than the inner ring 12 will be omitted, and only the features of the present invention will be described below.
【００１５】上記内輪１２の軸方向両端部（図１の上下
両端部）で内輪軌道３から外れた位置には、通油孔１
３、１３を、放電加工等により、上記内輪４の直径方向
に亙って形成している。上記各通油孔１３、１３の断面
形状は、両端の半円弧部同士を直線部で連続させた長円
形としている。そして、各通油孔１３、１３の長手方向
と上記内輪１２の円周方向とを一致させている。At both ends of the inner ring 12 in the axial direction (upper and lower ends in FIG. 1), at positions deviated from the inner ring raceway 3, oil passage holes 1 are provided.
3, 13 are formed in the diameter direction of the inner ring 4 by electric discharge machining or the like. The cross-sectional shape of each of the oil passage holes 13 is an ellipse in which semicircular arc portions at both ends are continuous with a straight line portion. Then, the longitudinal direction of each of the oil passage holes 13 and 13 and the circumferential direction of the inner ring 12 are made to match.
【００１６】尚、上記半円弧部の曲率半径をＲ1 とし、
上記各通油孔１３、１３の長さ寸法をＬ1 とした場合
に、Ｌ1 ＝（２．４〜９）・Ｒ1 とする事により、上記
各通油孔１３、１３の長さ寸法Ｌ1 が幅寸法Ｗ1 （＝２
Ｒ1 ）の１．２〜４．５倍となる様にする。各通油孔１
３、１３の断面形状をこの様に規制する事により、通油
孔を半径がＲ1 である円孔とした場合に比べて、各通油
孔１３、１３部分に発生する応力集中が、凡そ９０〜６
０％程度にまで緩和される。The radius of curvature of the semicircular arc portion is R 1 ,
When the length of each of the oil holes 13, 13 is L 1 , the length of each of the oil holes 13, 13 is determined by setting L 1 = (2.4 to 9) · R 1. L 1 is the width W 1 (= 2
R 1 ) is set to be 1.2 to 4.5 times. Each oil hole 1
By the 3 and 13 of the cross-sectional shape that restricts Thus, as compared with the case where the oil passage hole radius is a circle hole is R 1, the stress concentration occurring in each oil passing holes 13, 13 parts, approximately 90-6
It is reduced to about 0%.
【００１７】上述の様な通油孔１３、１３を形成した内
輪１２は、外輪及び転動体と組み合わせて、例えば前記
図８或は図１１に示す様な転がり軸受を構成する。この
様にして構成された本発明の転がり軸受により、通油孔
１３、１３を通じて潤滑油の供給を行ないつつ、内輪１
２に内嵌した回転軸を回転自在に支承する際の作用自体
は、前述した従来の転がり軸受の場合と同様である。The inner ring 12 having the above-described oil passage holes 13, 13 is combined with the outer ring and the rolling element to form a rolling bearing as shown in FIG. 8 or 11, for example. With the rolling bearing of the present invention thus configured, lubricating oil is supplied through the oil passage holes 13 and 13 while the inner ring 1 is being supplied.
The operation itself of rotatably supporting the rotating shaft internally fitted in 2 is the same as that of the above-described conventional rolling bearing.
【００１８】特に、本発明の転がり軸受の場合には、上
述の様に、内輪１２が高速回転した場合に上記各通油孔
１３、１３部分に生じる応力集中が、１０〜４０％緩和
されるので、これら各通油孔１３、１３部分に亀裂等の
欠陥を生じにくくなる。この結果、上記内輪１２をより
高速で回転させる事が可能となって、転がり軸受を組み
込んだ機械装置の性能向上を図れる。In particular, in the case of the rolling bearing of the present invention, as described above, when the inner race 12 rotates at a high speed, the stress concentration generated in the oil passage holes 13 is reduced by 10 to 40%. Therefore, defects such as cracks are less likely to occur in these oil passage holes 13 and 13. As a result, the inner ring 12 can be rotated at a higher speed, and the performance of a mechanical device incorporating a rolling bearing can be improved.
【００１９】次に、図３は本発明の第二実施例を示して
いる。本実施例の場合には、内輪１２の端部に形成する
通油孔１３ａの断面形状を楕円形とし、この楕円形の長
径方向と上記内輪１２の円周方向とを一致させている。FIG. 3 shows a second embodiment of the present invention. In the case of this embodiment, the cross-sectional shape of the oil passage hole 13a formed at the end of the inner ring 12 is made elliptical, and the major axis direction of the elliptical shape and the circumferential direction of the inner ring 12 are made to match.
【００２０】本実施例に於いては、上記通油孔１３ａの
長さ寸法（楕円形の長径）をＬ2 とし、幅寸法（楕円形
の短径）をＷ2 とした場合に、Ｗ2 ／Ｌ2 ≦０．９とす
る。これら両寸法をこの様に規制する事により、通油孔
を半径がＷ2 ／２である円孔とした場合に比べて、上記
通油孔１３ａ部分に発生する応力集中が９０％以下にな
り、その分だけ上記内輪１２の高速回転が可能となる。In the present embodiment, when the length (the major axis of the ellipse) of the oil passage hole 13a is L 2 and the width (the minor axis of the ellipse) is W 2 , W 2 / L 2 ≦ 0.9. By regulating these two dimensions in this way, as compared with the case where the oil passage hole radius is a circle hole is W 2/2, the stress concentration occurring in the oil passage hole 13a portion is below 90% Accordingly, the inner ring 12 can be rotated at a high speed.
【００２１】次に、図４〜５は本発明の第三実施例を示
している。本実施例の場合には、断面が円形の通油孔１
３ｂを、内輪１２の直径方向に対し傾斜させて形成して
いる。従って、この通油孔１３ｂの内輪１２の円周方向
に亙る断面形状は、上述した第二実施例の場合と同様
に、楕円形となる。この楕円形の長さ、幅両寸法を含
め、その他の構成及び作用は、上述した第二実施例と同
様である。Next, FIGS. 4 and 5 show a third embodiment of the present invention. In the case of this embodiment, the oil passage hole 1 having a circular cross section
3b is formed to be inclined with respect to the diameter direction of the inner ring 12. Accordingly, the cross-sectional shape of the oil passage hole 13b in the circumferential direction of the inner ring 12 is elliptical, as in the case of the above-described second embodiment. Other configurations and operations, including both the length and width dimensions of the elliptical shape, are the same as those of the above-described second embodiment.
【００２２】次に、図６は本発明の第四実施例を示して
いる。本実施例の場合、通油孔１３ｃの断面形状を、両
端の半楕円形円弧部同士を直線部で連続させた、長楕円
形としている。そして、通油孔１３ｃの長さ寸法をＬ3
とし、幅寸法をＷ3 とした場合に、Ｌ3 ＝（１．２〜
４．５）Ｗ3 となる様に、これら両寸法Ｌ3 、Ｗ3 を規
制している。通油孔１３ｃの断面形状をこの様に規制す
る事により、通油孔を半径がＷ3 ／２である円孔とした
場合に比べて、各通油孔１３ｃ部分に発生する応力集中
が、凡そ９０〜６０％程度にまで緩和され、その分だけ
上記内輪１２の高速回転が可能となる。FIG. 6 shows a fourth embodiment of the present invention. In the case of this embodiment, the cross-sectional shape of the oil passage hole 13c is a long ellipse in which semi-elliptical arc portions at both ends are connected by a straight line portion. Then, the length of the oil passage hole 13c is set to L 3
And when the width dimension is W 3 , L 3 = (1.2 to
4.5) W to 3 to become like, it regulates both of these dimensions L 3, W 3. By regulating the cross-sectional shape of the oil passage hole 13c in this manner, as compared with the case where the oil passage hole radius is a circle hole is W 3/2, the stress concentration occurring in each oil passing hole 13c portion, It is relaxed to about 90 to 60%, and the high-speed rotation of the inner ring 12 becomes possible by that much.
【００２３】次に、図７は本発明の第五実施例を示して
いる。本実施例の場合、通油孔１３ｄの断面形状を、内
輪１２の円周方向に長い長矩形としている。矩形の四隅
は曲率半径がｒの円弧部としている。そして、通油孔１
３ｄの長さ寸法をＬ4 とし、幅寸法をＷ4 とした場合
に、２ｒ≧０．３Ｗ4 で、且つＬ4 ≧１．２Ｗ4 となる
様に、これら各寸法ｒ、Ｌ4 、Ｗ4 を規制している。通
油孔１３ｄの断面形状をこの様に規制する事により、通
油孔を半径がＷ4 ／２である円孔とした場合に比べて、
各通油孔１３ｄ部分に発生する応力集中が、凡そ９０〜
６０％程度にまで緩和され、その分だけ上記内輪１２の
高速回転が可能となる。FIG. 7 shows a fifth embodiment of the present invention. In the case of the present embodiment, the cross-sectional shape of the oil passage hole 13 d is a long rectangle that is long in the circumferential direction of the inner ring 12. The four corners of the rectangle are arc portions having a radius of curvature r. And the oil hole 1
When the length of 3d is L 4 and the width is W 4 , each of these dimensions r, L 4 , W is such that 2r ≧ 0.3W 4 and L 4 ≧ 1.2W 4. Regulates 4 . By regulating the cross-sectional shape of the oil passage hole 13d in this manner, as compared with the case where the oil passage hole radius is a circle hole is W 4/2,
The stress concentration occurring in each oil passage hole 13d is approximately 90 to
This is reduced to about 60%, and the inner ring 12 can be rotated at a high speed by that much.
【００２４】上述の各実施例は、潤滑油供給用の通油孔
に本発明を適用した場合に就いて説明したが、本発明
は、図１２に示した様な、温度センサ設置用の凹孔１
４、１４にも適用できる。即ち、これら凹孔１４、１４
の断面形状を、上述した各実施例に於ける様な長円形、
楕円形、長楕円形、長矩形とする事により、内輪４が高
速回転した場合に、各凹孔１４、１４部分に発生する応
力集中を緩和できる。In each of the embodiments described above, the present invention is applied to the case where the present invention is applied to the lubricating oil supply hole, but the present invention is not limited to the case where the temperature sensor installation recess as shown in FIG. Hole 1
4 and 14. That is, these concave holes 14, 14
The cross-sectional shape of an oval, as in each of the embodiments described above,
When the inner ring 4 rotates at a high speed, the concentration of stress generated in each of the concave holes 14 can be reduced by making the shape oval, oblong, or oblong.
【００２５】[0025]
【発明の効果】本発明の転がり軸受は、以上に述べた通
り構成され作用するので、高速回転時に内輪に発生する
応力集中を緩和して、内輪の回転速度を高くでき、転が
り軸受を組み込んだ各種機械装置の性能向上を図れる。Since the rolling bearing of the present invention is constructed and operates as described above, the stress concentration generated in the inner ring during high-speed rotation can be reduced, the rotation speed of the inner ring can be increased, and the rolling bearing is incorporated. The performance of various machinery can be improved.
【図１】本発明の第一実施例を示す、内輪の部分平面
図。FIG. 1 is a partial plan view of an inner race, showing a first embodiment of the present invention.
【図２】図１の下方から見た図。FIG. 2 is a view as viewed from below in FIG. 1;
【図３】本発明の第二実施例を示す、内輪の部分平面
図。FIG. 3 is a partial plan view of an inner race showing a second embodiment of the present invention.
【図４】本発明の第三実施例を示す、内輪の部分平面
図。FIG. 4 is a partial plan view of an inner race, showing a third embodiment of the present invention.
【図５】図４のＡ−Ａ断面図。FIG. 5 is a sectional view taken along line AA of FIG. 4;
【図６】本発明の第四実施例を示す、内輪の部分平面
図。FIG. 6 is a partial plan view of an inner race, showing a fourth embodiment of the present invention.
【図７】本発明の第五実施例を示す、内輪の部分平面
図。FIG. 7 is a partial plan view of an inner race, showing a fifth embodiment of the present invention.
【図８】本発明の対象となる転がり軸受の第１例を示す
部分断面図。FIG. 8 is a partial sectional view showing a first example of a rolling bearing to which the present invention is applied.
【図９】第１例の転がり軸受に組み込まれる内輪を構成
する一方の半片を示す平面図。FIG. 9 is a plan view showing one half of an inner ring incorporated in the rolling bearing of the first example.
【図１０】図９の下方から見た図。FIG. 10 is a view as viewed from below in FIG. 9;
【図１１】本発明の対象となる転がり軸受の第２例を示
す部分断面図。FIG. 11 is a partial sectional view showing a second example of the rolling bearing to which the present invention is applied.
【図１２】同第３例を示す部分断面図。FIG. 12 is a partial cross-sectional view showing the third example.
１、１ａ 外輪軌道 ２、２ａ 外輪 ３、３ａ 内輪軌道 ４、４ａ 内輪 ５ 玉 ６、６ａ 保持器 ７ａ、７ｂ 半片 ８ 凹溝 ９、９ａ、１０、１０ａ 通油孔 １１ ころ １２ 内輪 １３、１３ａ、１３ｂ、１３ｃ、１３ｄ 通油孔 １４ 凹孔 DESCRIPTION OF SYMBOLS 1, 1a Outer ring track 2, 2a Outer ring 3, 3a Inner ring track 4, 4a Inner ring 5 Ball 6, 6a Retainer 7a, 7b Half piece 8 Groove 9, 9, 9a, 10 and 10a Oil passage hole 11 Roller 12 Inner ring 13, 13a, 13b, 13c, 13d Oil passage hole 14 Concave hole
Claims (1)
面に内輪軌道を有する内輪と、上記外輪軌道と内輪軌道
との間に転動自在に設けられた複数の転動体と、上記内
輪の一部に設けられた孔とを備え、上記内輪を回転させ
る状態で使用する転がり軸受に於いて、上記内輪の円周
方向に亙る上記孔の断面形状を、上記内輪の円周方向が
長く、軸方向が短く、且つ尖った角部を持たない形状と
した事を特徴とする転がり軸受。An outer ring having an outer raceway on an inner peripheral surface; an inner racer having an inner raceway on an outer peripheral surface; a plurality of rolling elements rotatably provided between the outer raceway and the inner raceway; A hole provided in a part of the inner ring, wherein in a rolling bearing used in a state where the inner ring is rotated, the cross-sectional shape of the hole extending in the circumferential direction of the inner ring is changed in the circumferential direction of the inner ring. A rolling bearing having a shape that is long, has a short axial direction, and has no sharp corners.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05177568A JP3114438B2 (en) | 1993-06-25 | 1993-06-25 | Rolling bearing |
| GB9412715A GB2279415B (en) | 1993-06-25 | 1994-06-24 | A rolling bearing |
| US08/266,267 US5399027A (en) | 1993-06-25 | 1994-06-27 | Rolling bearing for a high speed rotation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05177568A JP3114438B2 (en) | 1993-06-25 | 1993-06-25 | Rolling bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0712135A JPH0712135A (en) | 1995-01-17 |
| JP3114438B2 true JP3114438B2 (en) | 2000-12-04 |
Family
ID=16033248
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05177568A Expired - Lifetime JP3114438B2 (en) | 1993-06-25 | 1993-06-25 | Rolling bearing |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US5399027A (en) |
| JP (1) | JP3114438B2 (en) |
| GB (1) | GB2279415B (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19538553B4 (en) * | 1995-10-17 | 2010-01-14 | Schaeffler Kg | Rotor bearing of an exhaust gas turbocharger |
| JPH11182560A (en) * | 1997-12-16 | 1999-07-06 | Koyo Seiko Co Ltd | Rolling bearing device |
| JP2002130263A (en) * | 2000-10-31 | 2002-05-09 | Ntn Corp | Bearing with temperature sensor |
| NL1016756C2 (en) * | 2000-11-30 | 2002-05-31 | Skf Eng & Res Centre Bv | Measuring element for measuring radial and / or axial forces on a bearing. |
| US6511228B2 (en) * | 2001-05-08 | 2003-01-28 | Pratt & Whitney Canada Corp. | Oil annulus to circumferentially equalize oil feed to inner race of a bearing |
| JP2003028173A (en) * | 2001-07-19 | 2003-01-29 | I M N Kk | Rotating part support |
| JP4449920B2 (en) * | 2006-02-17 | 2010-04-14 | 株式会社安川電機 | Solid lubricated roller bearing |
| US8646983B2 (en) * | 2008-10-03 | 2014-02-11 | Jtekt Corporation | Rolling bearing |
| JP5426565B2 (en) * | 2008-10-22 | 2014-02-26 | 株式会社前川製作所 | Lubricated screw compressor |
| JP2010169247A (en) * | 2008-12-26 | 2010-08-05 | Ntn Corp | Railroad vehicle drive unit |
| JP5320281B2 (en) * | 2009-12-28 | 2013-10-23 | 株式会社ジェイテクト | Rolling bearing |
| DE102010035058A1 (en) * | 2010-08-21 | 2012-02-23 | Schaeffler Technologies Gmbh & Co. Kg | Lubricating oil supply device for a rolling bearing |
| EP2851502B1 (en) * | 2013-09-23 | 2015-11-18 | Sandvik Intellectual Property AB | Shank Adaptor with Fracture Resistant Flushing Hole |
| JP6645378B2 (en) * | 2016-08-03 | 2020-02-14 | 日本精工株式会社 | Ball bearings and spindle devices for machine tools |
| US10260563B2 (en) * | 2017-05-18 | 2019-04-16 | General Electric Company | Bearing cages for roller bearing assemblies |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2217801A (en) * | 1940-04-15 | 1940-10-15 | Katcher Morris | Bearing |
| US3195965A (en) * | 1961-10-25 | 1965-07-20 | Fafnir Bearing Co | Lubricating means for an antifriction bearing |
| GB1334454A (en) * | 1971-06-16 | 1973-10-17 | Timken Co | Roller bearings |
| US4108506A (en) * | 1976-10-26 | 1978-08-22 | Wrr Industries, Inc. | Bearing lubricating system |
| US4334720A (en) * | 1980-02-11 | 1982-06-15 | Industrial Tectonics, Inc. | Split-inner-ring ball bearing with lubrication structure |
| NL8503517A (en) * | 1985-12-19 | 1987-07-16 | Skf Ind Trading & Dev | SWING CIRCLE. |
| DE8711624U1 (en) * | 1987-08-27 | 1987-10-08 | Fag Kugelfischer Georg Schaefer Kgaa, 8720 Schweinfurt, De |
-
1993
- 1993-06-25 JP JP05177568A patent/JP3114438B2/en not_active Expired - Lifetime
-
1994
- 1994-06-24 GB GB9412715A patent/GB2279415B/en not_active Expired - Lifetime
- 1994-06-27 US US08/266,267 patent/US5399027A/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| GB2279415B (en) | 1997-05-07 |
| GB2279415A (en) | 1995-01-04 |
| US5399027A (en) | 1995-03-21 |
| JPH0712135A (en) | 1995-01-17 |
| GB9412715D0 (en) | 1994-08-17 |
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